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DUN uw NIOD INVENToRs'. MM2? GRoE/v W41. rsf? ME YER, BY Alva v vPatentedy Jan. 26,4 1.937

MACHINE 'rooL William F. Groene, Walter B.. Meyer, and George W. Luning, Cincinnati, Ohio, assignors to The B. K. Le Blond Machine Tool Company, Cincinnati, Ohio, a corporation o! Delaware Application May 7, 1935, Serial No. 20,220

31 Claims'.

^ Our invention relates to machine tools, and will be described in connection with a heavy duty lathe for turning the line bearings of crank shafts. 4

5 One object of our invention is` the provision of a novel construction for lathes particularly of the center drive-chuck type making for extreme rigidity and accuracy, and the rapid accomplishment of Aheavy work.

Another object of our invention, broadly stated, is to dispensewith hydraulic devices in machines of this character, and to use in the place thereof a system of electrical control of the times and rates of feed of the tools and the l5 work relatively to each other.

Certain advantages are gained over the hydraulic control and operationV in better adaptation of the feeding force to the Work, as this force is required to be'varied in the different stages of feed; and in the simplification of the machine by eliminating cumbersome piping, oftenrequiring movable joints, and involving the use of very complicated mechanism, together with control valves, relief valves, and the like,

and also requiring great care in regard to leakage from the hydraulic system. Power is being applied constantly to the uid, whether the machine is in-operation or not, whereas with the electrical control there is a use of power some- 3 what in direct proportion to the time during `which actual operations are being performed.

A particular advantage of our present invention over the usual hydraulic system, is in the case of the very slow rate of feed with correspond- 85 ingly heavy cutting force, near the finish of the cut; at-which time, with hydraulic feeding, slip- Vpage and leakage in the working parts may occur, especially after a considerable wear of the v parts and also to the change of viscosity of the 40 liquid. The rate of feed of the tools changes,

and sometimes the tools even stop without prop- 4 erly finishing the work, on account of these defects ofthe hydraulic system.

By our use of electrical control, with' the mechanim-`constructed for ready response tov such control, and especially with ample means`of adjustment to insure a maximum of accuracy in th operation of tools, we eliminate almost all bf the disadvantages of the hydraulic system ggg-above referred to, and gain a number of new advantages, as will be seen from the later detailed description.

Other objects of the invention are improvements in the feeding of 'the cutting tools, -the use of cam means for actuating the feeding means, said cam having various inclinations for producing coarse-feed, ne-ieed, and dwell of the tools on the work, electrically controlled.4 means' for producing effective feeding and rapid traverses of the tool actuating means, and effec- A5 tive braking during changes of speed, and improvements in means for. adjustably setting the tools. l

We have also improved machines of this character in respect of the coolant distribution. We 10 i provide substantiallycomplete immersion of the work and tools'in the coolant during the machining operation; and along with this there is adequate removal of. chips. We accomplish this, notwithstanding the irregular shapes .of the work 15 operated upon which heretofore, so far as we know has defeated attempts to provide an adequate immersion and removal of chips. By reducing splashing to a minimum, we attain that close 'application of the flowing coolant to the -chips which is necessary to carry them away and also that close contactwith the tools and work which is necessary to effect their proper cooling; and, of course, with a. minimum of splashing the' efliciency is increased and there 25 is less waste of thecoolant liquid, reducing not only the comparatively low cost of this liquid,

but especially the time required to attend to replenishing it in the machine.

Thev machine in which our invention is exemplified herein is similar to that disclosed in the patent to Groene et al., No. 1,934,976, of-November 14, 1933, application for re-issue of which Serial No. 748,720, filed October .17th,A 1934, is copending. The present embodiment resembles the above machine .in that there is a pairof tool -bars simultaneously moved in opposite directions for feeding to opposite sides of the work piece, fand these being mounted on a downwardly, forwardly inclined guiding support,` at the 401 forward lower end on which the work is mounted for the opposite approach of the .tool bars i andthe tools thereon. It will be understood, however, that we are notlimited, in the application of our present invention, to a. machine 45 of that type; our present invention being applithe patent to Groene et al., Reissue No. 18,662,

of November 22, 1932, in which that portion of .the machine 'which supports the tool bars is mounted on master cranks which have the same throw as and rotate in synchronism with the crank shaft which is being finished; the ma- -chine therein shown being hydraulically con-.

` closed and claimed in the patent to Groene No.

' by broken lines only. 4

usl

1,700,721, of January 29, 1929. We also illustrate in connection with the present example, chucks such as set forth in copending application, Serial No. 2,638 led Jan. 21, 1935. It will be understood, however, that we are not-limited to the details thus set forth and covered in other patents or applications. i

We accomplish these and other objects which will be clear to one skilled in the art upon reading these speciiications, by that certain construction and arrangement of parts roi which we shall describe an exemplary embodiment. Reference is made to the drawings in which:

Fig. 1 is a front perspective view of a lathe for turning crank shaft ,line bearings, emboxhving our invention.

Fig. 2 is a left hand end elevation of the same. 3 is a right hand end elevation of the same, the main driving motor being represented Fig.' 4 is a vertical front to line l-I of Fig. 1, a partial section also being taken on the line 4' -4 of Fig. 1, through one of the chuck mountings to show the driving means for the ring gear chuck.

g Fig. 5 is a plan view of the inclined top of the base of the lathe, clearly illustrating the feeding cam device.

Fig. 6 is a transverse sectional elevation, the section being on the line 5-6 of Fig. 2, illustrating the clutch control between the main driving shaft and the cam driving mechanism.

Fig. 'I is a left end elevation of the upper part of the mechanism illustrated in Fig. 6.

Fig. 8 is an enlargement of the lower vleft portion of Fig. 6, showing the clutchimechanism in section on the line 8-8 of Fig. 2.

Fig. 9 is a vertical front to rear section on the line 9--9 of Figs. 1 and 5, clearly illustrating the goolbarsandthecamdrivingmechanismthereor. -Fig.10isanenlargedsectionofpartofthe adjusting mechanism shown at the upper right in Mg. 9-on the line II-Il of F18. 9.

Fig. 11 is a detailedend view of the adjusting nut/showninFigiO." l

12 is a detailed end elevation of one of the feeding cranks with its segment.

Fig. 13 is a rearelevationof the same.`

Fig. Misarighthandendelevation ofpmof thecoolantsystemaporticn'ofachuckanda crankshaftthereinbeingshowntoclearly illustrate therelatioof the-coolantnozzles' to the crank shaft.

Eg. 15 is a fragmentary front elevation of the same.

Fig-1s a a longitudinal section crane of the coolant nozzles on the line I8'-I8 `of '15.

Fig. 17 is an enlarged sectional elevation, correar section on the responding to that in Fig. 9, showing the arrangement of the feed and traverse control limit switches.

Fig. 18 is arear elevation of thesarne,v taken along the line of inclination of the switch device, as shown in Fig. 17.

Fig. 19 is a plan view ofr the same on the same inclination.A 1

Fig. 20 is a front elevation of one of the remote control switch devices seen at the left in lthe middle upper part of Fig. 1.

Fig. 21 is a similar view of the other remote control switch seen at the right in Fig. 1.

Fig. 22 is a diagram of the electrical control connections.

Fig. 23 is a diagram illustrating the relation of equipped with centers but also has center drive chucks of the type which may be loaded by in- -serting the work throughthem.

I'he base I has a forwardly and downwardly inclined top, on the fr'o'nt lower end part of which the lathe center housings 2 are mounted. In order to mount these housings accurately in alignment, the base has a slot '3 in which is a block 3u, as seen clearly in Fig. 3, with `adjust` ing screws 4', the block being set in a slot in the base I, and the screws 4` engaging sides of a slot 5 in the respective housings 2. Afterthis adjustment is made, bolts 6, understood to extend through holes or slots in the housingsA 2 large Yenough to permitv this adjustment, and threaded into the base I, are tightened, xing the housings 2 on the base. Center pins 2a (Fig. 1) slide in the respective housings 2, and

are adjusted by hand wheels' 1,- having a conventional rack connection with the pins 2a. The pins 2a ythus may be run back and forth for loading and unloading the work.

Located between the housings 2 are the chuck housings 8 and the tool carrying units 25, 26. and 21. The chuck housings (which will be desoribedvilrst) are secured by bolts 9 to the forwardly downwardly inclined topof the base I, which bolts 9 pass through suilciently large holes in the housings 8 to permit slight-adjustment of the housings 8 in axial direction along the base I, before the bolts 9 are tightened; the location of the housings transversely being maintained by a key 9a. Each one of these chuck housings comprises a. main body part 8', which bears on and is connected to the base I, as just described, and extends substantially to the rear upper part of the base, where the key 9aislocated;andthisbodypart8'hasacap part 8 secured thereto by bolts 8', as best seen in Fig. 4.

The chucks are mounted in this chuck housing 8, the dividing line of the main part 8' and cap 8" being through the axis of the chuck.

Upwardly from and to the rear of the chucks, the main driving shaft III extends parallel with the chuck: axis and has bearings in the respecttive housings 8'. At the right hand end of the machine,asseeninFlg.1,adrivingmotorllis driven member I8 of the chuck has a peripheral) series of teeth Isa meshing with this intermediate gear I6.

The drivingmotor II is xed on a plate I3,4

held to the base I by bolts I9d through sufiiciently large holes in the plate to allow proper adjustment of the motor IIl radially to the main driving shaft gear I3 by adjusting means 20,'seen in Figs. 1 and 3.

The rear end of each chuck housing body 8'. has an extension with a bearing cap 2l secured thereto by bolts 22, for the respective line bearings 23 of a feed crank shaft 24, which determines the movements of tool holders which now will be described.

As here shown, (Fig. 1'), the machine is de signed to present three sets 'of tools to a crank shaft held in the chuck bodies IB, one between the two chuck bodies and the other two at respective outer sides of the chuck bodies.

Each set of tool bars is mounted in the respective housings 25, 26,` and 21 (Fig. 9) iixed to the base I by means of the bolts 23, allowing' adjustment of the unit along the base I parallel with the axis of the chuck before the bolts 26 are, tightened. The assembly of these tool barA housings and chuck housings is preferablysimilar to that disclosed and claimedin the Groene Reissue Patent No. 18,662, of November 22, 1932; in that the bolts 29 pass through the entire assembly of tool bar housings 25, 26 and 2l and chuck housings 6 and clamp them together; but the parts are so proportioned as to form a continuous mass of metal across the machine, to afford maximum rigidity of the chuck supports and the tool -bar supports relatively to each.

other. This is to say, the chuck housings and the tool carrying units are designed to occupy the space across the lathe and are machined to iit tightly together. No separating means are required. In this case, also, unlike the patent mentioned, the tool bar housings do not move relatively to the chuck housings; the tool bars sliding in the 'tool bar housings with motions determined by the feed cranks on the feed crank shaft 24.

Our'preferred construction of each tool bar housing 25, 26, and 21 comprises side plates 30, shown in Figures 3 and 9, with filler members 34, 35, .and 36, between them. The side plates 36 have extensions rearwardlyV ofthe filler members corresponding to the reamard extensions of the chuck housings, in which additional bearings 3I, with bearing caps 32 held by bolts 33, are provided for the feed crank shaft 24. I

Describing the middle tool bar housing 25, the filler members consist of the lower member 34, the narrow middle member 35, and the upper imember 36, providing two guideways for the tool bars 31 and 38, inwhich these toolbars slide parallel with the inclined.l top `of the base I. The lower tool ,bar 3I`which reaches downwardly and forwardly past the axis of the chucks, has additional guidance forwardly by a key 39 fixed in the lower filler member34 and tting in a longitudinalslot 4I! in thetool bar. The other twctool housings will be understood to be constructed in afsim'ila'rlmanner. Ouf-'account of the nature of the work, as here shown, the middle tool bar assembly is wider than either one of the outer ones, although it will be understood that we are not limited to such proportions, as these may vary with the nature of the work.

In this middle assembly we mount the rack 4 Ii which is included in the driving mechanism for 'the feed crank shaft.v For accommodating this rack 4I, the, lower filler member 34 has a slot 34a, the sides of which together with the top of the base and the top of the slot form a guideway for the rack 4I.

The feed crank shaft 24, (the purpose of which is to transmit the motion of the rack to the several tool bars in the several housings), has, preferably integral with it, a middle crank member 42. and at each side thereof, crank members 42 and 42", as shown in.Figure 13; each made up of spaced side members, and each. located in front-to-rear alignment with a respective set of tool bars. The middle crank 42 is provided with the gear segment 43;'(Figure l2),

l which meshes with the rack 4I, as shown in Figure 9; so that reciprocation of the rack 4I oscillates the feed crank shaft 24 and'its three cranks 42, 42' and 42".

Each one of these cranks has an upwardly extending arm and a downwardly extending one for connection, respectively, yto the upper and lower tool bar with which it is in front-to-rear alignment. This connection. .is effected by respective links 44 and 45; the tool bars 3l and 38 having, respectively, recesses 46 and 41 entered by these links, with pins 48 through the links and bearing in 'the side portions of the tool bars.

To connect the outer ends'of the links 44 and 45 to the respective crank arms 49 and 56, each arm has a crank pin 5| journaled in and extending across between its two side portions. Each crank pin 5I has a transverse threaded hole! into which is screwed a bushing 52 receiving the reduced cylindrical end part 53 of the respective link 44 or' 45, with a` shoulder 54 on the rod abutting the forward end of the bushing4 52.

The reduced end part of the link extends past the rear of the bushing 52 where it has threads 55 onto which is screwed nut 56 against the rear end of the bushing, and also a lock nut 57 against the rear side of the nut 56; which. lock nut 5l has a cotter pin 58 through it and the link rear end portion 59. as seen in Fig. 10.

The bushing 52 has a nange 60 on its rear end, which, as best seen in Fig. 11, has four slots 6I opening radially outwardly at frequent intervals;

and it also has grooves 62 extending around glliose parts of its periphery between thevv slots lock nut 51, and has a series`of projections 64 to enterl the slots 6I.of the ange 60, which projections have the slots 65 arranged to be continuous with the slots 62 of the flange when the projections are in the slot 6I of the ange; whereupon the continuous seriesof slots receive a snap ring 66 which holds the cup securely on the ange 60. 'Ihe outer endportion of the cup 63, past the end of the link portion 53, has a splinedsocket 61 which may receive a splined wrench. Bythis means, thev bushing 52 may be turned in the pin 5I, moving forwardly or rearwardly relative thereto because of its thread- A cup 63 nts around the nut 56 and the` 44 or 46, with the result of adjusting the corresponding tool bar forwardlyor rearwardly relatively to the feed crank shaft 24. Although this adjustment may thus be readily effected, the nut 56 may be so adjusted and held by the lock nut 51 and cotter, pin 58 that there is practically no lost motion between the link and the feed crank. Thus the tools may readily be adjusted for proper cutting with respect to each other and for ultimate depth of cut.

On the front ends of the tool bars'31 and 38 -are carried, respectively, ,the tool holders 68 and 68a, holding the tools 68' and 68", respectively; the lower tool bar 31 moving rearwardly and the upper tool bar 38 moving forwardly, to feed these tools 68' and 68 respectively, to the work W held in the chucks I8; as may be clearly seen in- Fig. 9. This describes only the middle set of tool bars and tools; but it will be understood that the other two sets work in the same manner; all tools being fed uniformly by `the feed crank shaft 24 and its unitary crank arms connected to the tool bars by the links as above described; and as oscillated by the meshing ofA the rack 4| with the gear segment 43 of the middle crank arm.

It is the purpose of the mechanism now to be described to effect the oscillation of the feed crank shaft 24 and feed cranks to provide those rates of feed of the tool bars and tools toward the `work W which are desirable at different stages of the feeding operation, as well as to withdraw these from the work when the operation is completed.

The main drive shaft |8 projects to the left of the left hand tool bar housing 21, in which it has a bearing, as before described, and has fixed on it a pinion 69 and a sprocket wheel 18, as shown in Figure 6. To the rear of and4 below the shaft I8, a. transmission shaft 1| has one end journaled in a bearing 12 in the tool bar housing 21, and is journaled near its other end ina bearing 13 in a bracket 14 xed on the base I. A gear 15, xed on the transmission shaft v 1|, meshes with the pinion 69. At the rear of this gear 18, a plugging relay PR is fixed to the side of the housing 21, and has a small gear 16 meshing with the` large gear v15. A limit switch LS-4 is mounted on the bottom of the plugging relay casing, land has an actuating lever 11 with a roller, which is engaged 'once at .each revolutionof the large gear 15 by a cam plate 18 xed on one side of the gear. This cam plate is slotted, with a screw 18' through its slot into the gear 15, so that it may be adjusted circumferentially of the gear for timing the actuation of the limit switch LS-4 (see also Figure '1). The

.ratio between the pinion 69 and the large gear 15 is the same as that between the pinions |5 and the gears constituted by the teeth |8a on the chuck bodies .|8; so that the gear 15 rotates operative connection between the shaft 1| and the rack 4| that actuates the tool bars, and the tools carried thereon, toward and from the work W. This mechanism includes a ,cam actuating the rack 4|, and a screwwhich moves the cam.

Where the shaft 1| projects past its outer bearing 13, it has a pinion 19 removably held on it by securing mears including the nut 19'; so that this pinion can be removed and a pinion of different size substituted. Meshing with this pinion is a gear turning on a stud 88a which vis clamped by, a' nut 88h in a vslot 8| in the upper part of the bearing bracket 14 (see also Figure 2). A This gear 88 meshes with a, larger gear 82 down at the rear; and the slot 8| is curved concentric with the axis of this last mentioned gear 82. 'I'he gear 88 thus may be mounted anywhere along the slot 8| in accordance with the diameter of the pinion 19 or any dierent sized pinion substituted therefor.

The feed screw 83 (Figures 5, 6 and 8) is journaled ina bearing 84 `on the end part of the base capable of sustaining both radial and axial thrust loads, and in an outer bearing 85a in the lower end of an arm 85 which is screwed to the upper part of the bracket 14 and depends some 'distance out therefrom. The

as the feed screw is rotated in one direction or the other, the cam plate 86 is slid in one direction o r the other; it being understood that the feed screw 83 is so mounted in its bearings that it has no appreciable movement in an axial direction. A roller 98 rotatable upon a stud 9| depending from the rack 4| (Figures 5 and 9),

is received between the'cam bars 92 screwed' to the top of the cam plate 86. These cam bars 92 have their faces with which lthe roller 98 contacts inclined in various degrees to the direction of sliding of the cam plate 86; so that sliding of the cam plate will slide the rack bar forwardly or rearwardly and operate the feed crank 24 accordingly, with rates of advance or withdrawal of the tool bars depending upon the angles of inclination of the cam bar surfaces.

Next to the bearing 84 is a grooved pulley 93, having a long hub-94 held to the feed screw 83 by splines 95, as seen in Fig. 8. This hub 94 carries pins 96 projecting outwardly therefrom parallel with the axis; and surrounding and free to rotate on this hub is the large gear 82 previously referred to as being driven from the main driving shaft |8 through the gearing above described. A pressure plate 91 is mounted on the pins 96 of the pulley 93; and between this plate 91 and the gear 82, and between the gear 82 and the adjacent side of the pulley 93, -respectively, are sets of friction discs 91a, which, when the pressure plate 91 is forced inward, will cause the gear 82 to rotate with the pulley 93 and the feed screw 83. Normally, springs 98 yieldingly hold this pressure plate 91 outwardly,'so that the gear 82 is free to screw 83.

The hub94 of thepulley 93 extends out beyond the pressure plate 91 and is threaded externally and has screwed on it a spider 99 with arms on which respective levers |88 are fulcrumed at |8|; each lever having a lug |82 bearing against a respective vpa'd |83 on the outer face of the pressure plate 91, in such a manner that spreading of the .opposite ends of these levers |88 radially out- /For operating these levers |68, a head |84 is' slidably keyed at |85 on the" screw 83, and is rotate relatively to the feed screwed into a spider ,which has arms |86 which,l

are connectedl by links |81 and pins |88 and |89 t-o the outer ends of the levers |88, to have a toggie action for spreading the -levers radially outward when the head |04 is slid in toward the clutching device. This head |04 extends out from its threaded connection with the spider and has bearings H0 in`a collar III; which collar is straddled by and pivotally connected at |I0 to the members of the forked lower end part II 2 of the actuating lever 3, which extends upward and has its iulcrum I I4 in the inner end parts l 10 Iofjlinks ||5 which are pivoted at I I0 to the previously described depending arm 85 that has the cuter bearing 85a for the feed screw.

That part of the bracket 'I4 inward from the mounting of the arm 85 has the form of Ha table i|1 with a side member IIS inclining upwardly and outwardly, at its rear edge. This table II1 supports two solenoids ||9 and |20, having movable cores |9a and I20a, respectively, projecting from their tops. On'the top portion of the rear side member H8 a. T-shaped three-armed lever I2| has the fulcrum |2Ia at the junction oi its three arms. Two arms |22 and |23 project in lopposite difections and are connected by pivoted links |24 and |25 to the solenoid cores ||9a and I20a, respectively. The third arm |276 extends lupwardly and is connected to the upper end part |21 of the actuating lever H3 by a link I28, which preferably has provision at |29 `for adjusting its eiective length. j

A limit switch IS-'S is mounted on the inclined face of the side member II8, and has its operating lever |30 so positioned that this limit .switch is actuatedi as the three-armed lever swings its inner arm |23 downward, by the engagement, with this limit switch lever, of a pin |3| in an upstanding lug on the lever arm |23.

The grooved pulley 93, previously referred to' as beingsplined at 95 to the feed screw 83, is operatively connected by belting |33 to the pulley |30 of the motor |35 mounted on the rear side of. the base'i (see Figure 5). The purpose of this motor' |35 is to advance the tools rapidly to cutting position and rapidly return them after each cutting operation. 'I'he actual feeding of the tools to the work is euecte'd when the feed screw 83 is clutched to the gear 82 by the clutching'means comprising the friction discs 91a and operated through the lever ||3 and link |28 from the lever |I1, when the solenoid ||9ls energized, so that driving force is applied from thevmain motor II through the main shaft I0. 'I'he rapid Vtraverse -motor |35 is under control of, limit switch'LS-S, which'switch leaves open the circuit of this motor |35 unless descent of the pin I3| Awith the lever ||'|l when the other solenoid |20 is energized to unclutoh the feed screw 83 from the gear 82.

lThe result of this arrangement is to give to the clutch device a braking function, which will prevent over running by bringing the speed of the feed screw 83 and pulley 93 down to the speed of the gear 82, which can control the. speed of these parts by its connection through the gearing 8D, 18, 15,59 and main driving shaft l0 t0' the motor Ii, because of the high ratio of this gearing.

dThe feed cam device, operated by the feed it is tripped by the pending from a mid-length portion of the cam plate 86 that this switch lever |31 will be thrown one way or the other in the course of an intermediate part of the travel of the cam plate. The other two switches LS-I and JIS-3 are of such construction that they are normally closed, and they have levers |39 and |40, with upstanding rollers |4| and |42, which are engaged by bars |43 and |44, respectively, to open the respective switches in the course of terminal portions of the travel o f the feed cam plate 86.

The electrical system comprising the several 'electrical devices, 'including the solenoids I|9 A frame |41 supports loading and unloading devices |48 and 49, comprising depending hook members |50 and I5! to engage the work pieces W.y The bodies of the chucks I8 are adapted to allow passage of the work piece W through them;` the hook members |50 and |5| being U- shaped for the purpose. Such loading and unloading devices not being parts of the present invention, but being fully set forth and claimed in Patent No. 1,700,721 dated January 29, 1929,

. it is not necessary to further disclose them herein. The chucks shown herein are of the type disclosed and claimed in co-pendng application Serial No. 2,638 filed Jan. 21, 1935.

Our presenti machine also comprises novel means for cooling the tools and flooding the tools and work piece with liquid for efficient removal of the chips; and this apparatus includes a pump operated by an electric motor which also is includedin the above'mentioned electrical system, with control meansfcr this motor also included in the control station |45.

This coolant and flooding apparatus (see Figures 14,*15, 16, and 3 and 5) comprises a pump 152 mounted on the lowerV part ofthe rear side of the base I with its shaft vertical and directly connected to its driving motor |53, mounted on the rear 'side of the base I above the pump |52. The intake port |54 and discharge port |55 of this punip enter, through the base of the pump, the water and chip chamber |58 in the bottom of the base I, close to the bottom of said chamber, insuring that the pump |52 is always primed.

The intake port |54 leads from the chamber |56 directly into the pump |52. A pipe |51, as seen `in Fig. 5, leads forward from the discharge port of the pump and turns to the left; and at the middle of the machine extends forward and has branches |58 and |59` leading to the left and right, respectively, and then forward and ,upward into respective heads |60 and IGI `forwardly from and somewhat below the transverse plane of the axis of the chucks I8. This device 'is not illustrated in Fig. 1, because it would obscure this illustrationr of the chucks and the tool bars andtools; but as will be seen in Fig. 5, the pipes |58 and v|59 -are close to the respective sides of the forwardly 'extended p0rtion |62 of the water and chip reservoir; so that it will be understood that 'these heads |60 and il are m from: of the lathe centers 2a; being so positioned to support between them the structure through which these heads discharge the .coolant liquid to the portions of the work piece Wand thetools Aoperating thereon, between the brackets.

chucks I6 and at the outer sides of these chucks. This relation is indicated in Fig. 15, where the work piece W is shown held on the centers 2a; and the structure between the heads and |6| is shown in its relation to the work piece. Only the front portions of the chuck housings 8 are shown, their portions that would surround the work piece being omitted. i

This structure comprises two manifolds |63 and v|64, extending parallel with the axis of the chucks, and having their ends so connected to the respective heads |60 and |6| that they may` individually be rotated in the heads but will make liquid tight connection with the heads at and |66, respectively. These manifolds |63 and |64 are supported by brackets |61 and |68 xed on and extending forward from the respective chuck housings 8; and it will be understood that the supply pipes |58 and |59, thus connected to the manifolds are also supported by these These brackets are in the form of clamps, each with an outer section |61 or |68' clamped to the main portion |61 and |68 of the brackets by clamp screws |60., In this manner, each manifold may be clamped tightly enough to -prevent itsv turning accidentally, yet may be lturned when required.

coolant liquid lto those portions of the work piece at the outer sides of the chucks. A third nozzle |1| in like manner extends from the middle of the upper manifold |63 to discharge Vto that portion of the work piece W between the chucks.

The lower manifold |64 has a similar set of nozzles |10' and |1.|' which extend upwardly and rearwardly with Ytheir discharge ends somewhat below the horizontal plane of the axis of the chucks. These lower nozzles are shorterr than the upper nozzles, as may be seen in Fig. 9i being 'limited in length owing to the forward projection' of the lower tool bar 31,A its head 68 and the'tool 68' held thereon, as in Fig. 9.

, The upper manifold |63 has integral with it a lug |12 through which is screwed an adjusting screw |13 bearing against the chuck casing 0; and the lower manifold |64 has a lug |12' integral with it, through which is screwed an adjusting screw |13', bearing against the adjacent lower side of the upper manifold |63. By these adjusting means, the manifolds and the nozzles extending therefrom may be nicely adjusted to discharge the coolant liquid onto the work piece W and the tools in exactly the required relation thereto. At the` same time, this adjustment does not hinder the ready swinglng of the nozzles |10 and |1| forwardly away from their operating positions to-aiford easy access to the work piece W and the tools, should inspection or adjustment be found. necessary at anytime.

vEaclrone of the dischargelnozzles |10 or |1| or |10' or |1|', is carefully designed to discharge a flood of coolant liquid of large volume, but at a slow rate, without bubbling orsplashing of the liquid. This results in streams of liquid so oontinuous and voluminous as to amount to a total submergence of the tools and the work.

-The attainment of this result is aided by the provision of a baille |14, in each nozzle, which is seen in Fig. 16, having a hinge |15 connecting it to a bottom wall of the nozzle near .the junction of the nozzle with the manifold, and extending toward the discharge end of the nozzle for some distance, and being yieldingly held down by a spring |16, against an adjusting screw |11 threaded through the bottom wall of the nozzle, by means of which-screw the baille |14 may be more or less projected across the passage through the nozzle. yBy this means the volume of the flow of liquid may be very nicely adjusted while the nozzles are in operation, and while the operator may clearly observe the action of -the stream discharged from the nozzle.

We nd that the proper flow of coolant liquid is well attained by having the nozzle of rectangular cross section at' its outlet; the width of which, of course, is dependent upon the axial length of work piece and tools to be'ooded; asl

for instance, in Fig. 15, the two outer nozzles |10 are much greater in width than the middle nozzle volume at relatively slow speed; and, of course,

with the middle nozzle |1| this same result is attained as nearly as possible, consistent with the limited space permitted for this nozzle. This explanation will be understood to apply equallyv to the lower manifoldA |64 and its nozzles. Also, it will be understood that, while we have found in a particular instance, an advantage for the shape and proportion of the nozzle justexplained, this is not to be understood as limiting. Certain variations in shape and proportion will occur ofcourse, in conjunction with the operation upon work pieces of different proportions, and with tools accordingly disposed. VThe illustration 'of the preferred shape and proportion-in conjunction with the particular work piece il-v lustrated will, however, indicate the nature of our invention in respect to the discharge of coolant, and the elcient removal of chips by the coolant as it flows awayfrom the work piece and tools.

We have mentioned, as occasion arose, each one of the electrical devices involved in the operationof the machine; and for a clear explanation of the correlation o f these devices with each other, as well as with those parts ofthe machine the operations of which they effect, we refer to .the diagram in Fig. 22, illustrating the wiring connections for the electrical system, and also to the diagram in Fig. 23, which clearly illustrates the nature of the operations to be elected in the course of a cycle of operations of the machine,

under the control of the electrical system.

The understanding of the electrical system will be facilitated by rst considering the series of operations to,be effected under the control thereof, as illustrated in Fig. 23. In this diagram the tool b'ars, the feed crank and their link connections therewith are shown; as also is the segment on the feed crank, the rack meshing therewith and an outline of the slot of the cam plate in which the rack roller engages; as well as the feed screw, its threaded connection tothe cam plate and its drive mechanism.

The travel of the cam plate has divisions indicated as for rapid traverse to work, travel for coarse feed, travel for fine feed, stationary condition for dwell, and rapid return to position for with, it will be seen that there is a modification introduced between the effects due to cam travel and the actual travel of the tool bars and tools.

`the dimensions downwardly inclined to the right;

and in terms of travel of the rack 4| by the dimensions at right angles to those just mentioned;

in the lower part of the diagram. Corresponding motions of the feed crank are indicated by angularly separated lines up to the left; and heavy broken lines indicate positions o'f the connecting links during a nal -stage of tool feedingoperation. Down at the left, dimensions indicate the actual tool bar and tool travel.

It 'will be observed from this diagram that there is rst .a rapid traverse'of the tools toward the work, not lonly due to the angle of the cam, but because the drive is then by the rapid traverse motor |35;` then two stages of actual cutting travel, the first of which for coarse feed, is of less time duration than the second travel for fine feed, but which .has a rate of forward movement of the tool bar and tool, which `while considerably slower than the rapid traverse', is

considerably faster than the travel for fine feed.

of travel of the tools, in the several stages, areprimarily determined by the inclinations of various portions of the cam slot to the line of itsl travel, and by the extent of these variously inclined portions of the slotk along the plate in the general direction of its travel. By reference to the indications of the different stages1of swingingv of the feed crank and its links there- 'I'his -is due to the fact that although the rack and segment connections between the cam plate andthe feed.4 crank uniformly transform the rectilinear motion of the cam plate to the rotary motion of the feed crank, the anglefof each arm of the feed crank and its respective link varies in the course of swinging of the crank, and there is diminution of the feeding motion of the tool bars andtools relative-to that of the feed cam as the crank arms more nearly approach positions ofalignment with thelinks.

By reference to the indications of angles and arcs in the upper part of the diagram, it will be seen that the actual rapid traverse to the work and coarse feed are nearly equal in length, but the fact will remain that -the rate vis much less, during the coarse feed than during'the rapid traverse; :and it will be seen that the rate of iine feed is very much less than either of these, owing to the approach to alignment of the links and crank arms. Y

It will further bey understood that there is an increasing toggle effect as the crank arms and links approach alignment; with\ a. correspondingly greatly increased mechanical advantage in the transmission of the feeding force to the tool bars and tools by the feed crank and its driving feed cam and feed screw.' 'I'he rapid return, of course, partakes of the variations in rate of travel due to the different directions of the cam plateA slot; but this is made far more rapid, by the introduction of the vrapid traverse motor |35 into the operation upon completion of the finishing' operation, as has before/heen referred to.

with a main 'une switch (not shown) as is usual. Remote control push button and selector,

switch stations are conveniently located for the operator at |45 and |46 (Fig. 1). With the selectors |18 and |19 (Fig. 20) in the manual and traverse-off positions, respectively, the main line switch may be closed. With the se- 1ector switch ist in the "feed-on" position, the rapid traverse motor |35 (Figs. 2 and 6) can now be jogged in either the forward or reverse direction, by turning the top selector switch |'|9 in the proper direction. In this manner limit switches LSI and LS3 (Figs. 15, 16 and 17.), can be checked to be sure that their settings are correct to protect the traverse motion against overtravel in the reverse or forward directions. Limit switch IS2 can also be checked to see that it operates in the forward direction at the point where the tools 68' and 68" normally start to engage the work (Fig. 23). f

With the selector switch IBI (Fig. 21) in the jog position the main drive motor (Fig. 3) may be jogged by operating the jog push button |82. To check the adjustment of the plugging relay PR and the setting of limit switch LS4, (Figs. 8 and 9) the "jog-run selector |8| (Figs. 21 and 22) can be turned'to the Vrun position,. and the "run" pushbutton |83 pressed. After the main drive motor has accelerated to full speed the stop push |84 bute ton may be pressed and the stopping position of the chucks I8 noted,'it being necessary to stop the work holding chucks I8 at a predetermined position in order to facilitate loading and un- J loading of the work W. Since the gear 10 (Figs. 8 and 9) rotates in synchronism with the two chucks. I8 as before described. a definite relationship is automatically established between the desired stopping position of the center drive chucks and the proper location of-actuating vdog 18 for limit switch L84. For this, the adjustment 18' is provided so as to allow a nice 'final adjustment of the exact stopping point of the chucks. The plugging relay PR, should be adjusted so that plugging contactor SP (Fig. 22)

opens, just as the motor comes to standstill and before it starts in the reverse direction.

With bottom selector4 switch |85 (Figures 20 and 22) 'turned to the pump on"position and the selector switches |18 and` |88 set at automatic and feed on positions respectively (Fig. 23), the lathe is' ready for an automatic cycle. Pressing the run push button |83 (Figs. 21 and 22) picks up control relay CR!l (Fig. 22) which starts the coolant pump |52 and the main drive motor Contactson relay CR! energize coil CRI which in turn causes solenoid contactor F to pick up, de-energizing the on solenoid ||9 and energizing the oifv solenoid |20 (Fig.

7), which disengages the feed clutch mechanism, as already described, throwingthe main feed' oi. Bell crank is thus rocked to the right and, through the means |3|, as described.

closes limit switch LS5, and with relay CRI (Fig. 22) closed, contactor TF closes. energizing the rapid traverse motor. |35 in the forward direc.- tlon. When limit switch I SZ (Figs. 15 and 16) is tripped, relay CRI is opened, which stops the rapid traverse motor |35 and opens contactor F. causing the olf solenoidu|28 to be de-energized and the on solenoid ||8 to pull the feed clutch back into engagement. v

When the cam plate 88 and tools 88' and 68" lare fed forward suiliciently to trip the limit switch LS3, (Figs. 15 and 16) .relay CRI (Fig.

22) opens, stopping the spindle motorand. energizing relay CR-3. This relay in turn energizes contactor F which changes the control circuit to again allow the on solenoid (Fig."l) to pull the feed clutch open, closing limitA switch 185 and energizing the reverse traverse contactor TR.

The cam plate and tools then rapidly traverse back to the starting position where limit switch LSI is tripped, de-energizing relay CRI and traverse contactor TR. As soon as relay CRS '.opens, contactor F again opens, the feed clutch is re-engaged serving as a brake to prevent overtravel of the cam plate and the tools.

It will be noted as already described that `the control is arranged so it is impossible to energize the rapid traverse motor |35 unless the selector switch is in the "feed on position to be sure that the feed clutch will be automatically engaged as soon as the traverselmotor is de-energized so as to prevent excessive coasting in either direction. h

'Ihe control is also arranged so that 1f the tools are permitted to feed up to the point where limit switch LS3 is tripped, under manual `o p-` eration, relay CR! is tripped as it is under automatic operation, stopping the main drive motor and thereby preventing overtravel.

The traverse selector switch |19 (Figs. 20 and 22) has no control function during the automatic cycle, and may be left in any position although it is usual to leave it in the traverse-o 'f position to avoid a surprise operation when the manual control is selected.

During the automatic cycle, by turning the bottom selector switch |85 (Figs. A20 and 22) to the pump-off position, the coolant pump |52 may be stopped momentarily to arrest the ilow of coolant onto the work and tools for inspection of the machining operation.

Dm'ing automatic operation, pressing the stop" button |88 at any time will stop the main drive motor and chucks I8 and cause the tools immediately to traverse back to the starting position. Y

An interlock on the spindle running contactor SR prevents relay CRI being closed on the vautomatic cycle unless the main drive motor is running, so that rapid traverse motor |85 is thereby prevented from running the'tools up to the work should the main drive motor contactor Y be opened for amr reason. I

The sprocket wheel 18 on the main driving shaft I8 has a chain |85 which runs .around a sprocket |81 on the shaft of a lubricant pump |88 which is mounted on the top of the adjacent chuck housings 8. Outlets |88 lead from this pump and willAbe understood to have suitable Abranches to the various bearings of the machine, so that the pump forces lubricant into the bearings at all times when the machine is running It be seen that the principle of the improved machine permits a great range of variation in the proportions between roughing cut feed, finishing cut feed, dwell. and traverse to lbeginningoi! cut and traverse from completion of cut back to initial position. Factors contributing to these proportions are the inclinations of the several parts of the cam grooves'formedbetween the cam bars 32, the relative lengths of the two arms of each set in the feed crank 24, and also the normall operating speed of the traverse motor |35, relative to that derived from the operativeconnection to the main driving shaft which drives the chucks. Thus, different claim as new and desire to inclinations can be given to the cam bars 92; the arms of the feed crank 24 need not be of the same length; the relation of the links 44 and 45 to the feed cranks may be varied, changing the variation in rates of feed at different stages and modifying the toggle action in the final stages. This toggle action is especially valuable -in relieving the parts ofthe machine of undue strain in the iinal cutting stages, where steadiness of the machine parts is especially 'important because of'the need of steady application of the tools to the work for correct and accurate n' ish. l

Having thus described our invention, what we secure by Letters Patent isz- 1. In a machine of the character described, comprising a rotatable work holder and a tool holder related for relative feed or withdrawal of the `work and tool, means for rotating the work holder, and means for causing said relative feed and withdrawal, said means for rotating the work holder being electrically driven, means op.

erating in conjunction with the rotation of the holder to causeY feed Vof a tool to work held in the work holder or withdrawal of the tool from said work,.an element rotating in conjunction with the rotation of the work holder, mechanism operatively connected to the tool holder to cause its-feeding and withdrawing movements' driving means `having a source of energy independent of the source of energ; for rotating said work holder and said element, .means for connecting said mechanism to said element for driving said mechanism in proportion to the rate of rotation of said element, or releasing said mechanism from said element, said connecting and releasing means being eiective, upon release. to bring said mechanism under the faster driving action of said driving means.

3. A machine as set forthin claim 2, in which the mechanism comprises a cam device operative on the tool holder and a screw operative upon the cam device and subject, alternatively, to the driving actions therein specified.

4. A machine as set forth in claim 2, in which the mechanism comprises a cam device operative on the tool holder and a screw operative upon the cam device and subject, alternatively, to the' driving action therein specified, said mechanism also including, as a connection between the cam device and the tool holder, a crank related to the connecting the crank tothe tool holder and varying the' rate of movement of the tool holder toward the work as the angular relation of the ycrank and the link varies. Y

5. A machine as set forth in claim 2, in which the mechanism comprises a cam device operative on the toolholder and a screw operativeupon the v earn device'to be oscillated thereby, and a link cam device and Subject, alternatively, t0 the driving action therein specified, said mechanism 

